Governing mechanism



F. H. VAN NEST GOVERNING MECHANISM Filed May '7, 1958 2 Sheets-Sheet 1 I lhventor-l: Francis PIA/ah Nest His Attorney.

1941. F. H. VAN NEST 2,253,963

GOVERNING MECHANISM Filed May '7, 1938 2 Sheets-Sheet 2 Patented Aug. 26, 1941 Francis H. Van Nest, Saugus, Masa, assignor to General Electric Company, a corporation of New York Application May 1. 193s,..sena1 No. 206,617

The present invention relates to governing mechanisms as may be used for controlling elastic fluid turbines or like prime movers in response to changes of an operating condition, for instance in response to changes in speed of a machine or pressure in an extraction stage or exhaust stage of a turbine. More specifically; the invention relates to governing mechanisms with variable regulation. Ordinary governing mechanisms usually have positive regulation, that'is, in case of a pressure governor they permit for example a gradual drop in pressure as the load increases from no load to full load, while in case of a speed governing mechanism they permit a gradudlglrop. inspeed of a prime mover as the load on-"the prime mover increases fromno load to fulllpqgi gfiThere are cases where it is desired to maintain pressure or speed constant, irrespective of variations in load. This is accomplished by the provision v of a governing mechanism with zero regulation. There are'other cases where a flxed negative regulation is desired which in the case of a pressure governing mechanism means that the pressure should rise as the load increases. The general object or'my invention is to provide an improved .governing. mechanism with variable regulation whereby such mec'h can be readily'adjusted to obtain any degree of positive and-negative regulation orzeroflregulation.

For a consideration or whatI believe to be, novel and my invention, attention is directed to the following description and the claims appending fluid to a hydraulic motor IS. The latter has a piston lS-with astein connected to the valve I I and to the right-hand end of the floating lever it. During operation an increase in pressure in the exhaust conduit l2 causes through the governing mechanism I3 upward movement of the controlled element. [5 whereby the pilot valve I! is moved upward and permits the flow oi operating fluid to the upper side of: the piston l9, thus forcing the piston' 19 downward and resulting in closing movement of the valve II and drop in 'ments moveln opposite direction to pressure in the exhaust conduit l2., Downward movement of the hydraulic motor piston with its stem 20 causes through the follow-up lever l6 downward movement of the pilot valve I1, thus restoring the lat er to its neutral position. A drop in pressure in the exhaust conduit lzcauses similar operation except that the various eleopen the turbine inlet valve I I.

Let us assume the pressure in. the exhaust conduit y l2 is 50 lbs. per square inch' at no load. The governing mechanism l3 may be adjusted so that the pressure of 50 lbs.- is, maintained as the load increases from no load to unload or the governing mechanism may be adjusted so that the pressure of 50 lbs. changes gradually as the load on the'turbine or the flow through theexhaust l2 increases from no load to full load.

The governing mechanism comprises a casing 2| with a cover 22 securedto the casing by bolts ed thereto in connection with the accompanying drawings.

In the drawings Fig. 1 illustrates a diagrama sectional detail viewot the governing mecha-/ nism. The'arrangement of Fig. 1 comprises an elastic fluid turbine 10 which has an inlet valve H for controlling the flow of elastic fluid to the turbine, and an exhaust conduit I2. The turbine is non,- condensing, the elastic fluid discharged through the exhaust conduit being used for heating or other industrial purposes. In such cases it is desirable to maintain a certain pressure fin the exhaust conduit during varying load conditions. To this end I provide a governing mechanism I: which is subject to the pressure in the exhaust conduit I2 througha pipe H. The mechanism has a controlled element l5 connected to thel rthand end of a floating lever l6. -An interme late point of the floating lever I6 is connected to a 23?? The pipe is connectedto a device responsive to changes in a condition to be controlled. In the present instance the pipe ll/ is connected to a pressure responsive device 24 which has a casing 25 secured o the cover 22 by means including bolts 26. l e sp'onsive device has'bellows 21 with a lower end secured t a flange 28 of the cas g and an upper end closed by a plate 29 form ng a'seat for a conical pivot bearing 30. "The pivot bearing 30 is connected by'a link 3| having pivoted ends to a conical pivot bearing 32 of a governor lever '33.

The lever 33 is fulcrumed on a conical pivot bearing 34 which in turn is secured to the cover, 22

by bolts 35. The lower side of the lever forms a conical pivot bearing fl'whlch is connected by an adjustable link to a variable orifice or a cup valve 38 in cooperative relation withthe discharge end'of-a channel 39 formed by a 'tube 40. The connection between the cup valve 38 and the lower end ofthe link 31 includes a conical pivot bearing II on the upper side of a flexible pilot valve I! for controlling the flow oi operat- "t5 diaphragm or leaf spring 42, which latter is secured by screws 43 to brackets 44 formed at pressure rethe upper end of the tube 48. The pivot bearing 4| is screwed into a member 45 engaging the lower side of the diaphragm 42 and provided with a spherically-shaped extension engaging a spherical recess 48 in the cup valve 33. The channel 39 communicates through a channel '41 with a hydraulic motor 48. The latter has a bellows 49 connected at its upper end to a flanged cylinder 58 supported on the casing and secured thereto by means including a cover and bolts 52. The lower end of the bellows 49 has a bottom plate 53 with a conical pivot bearing 54 engaged by the conically-shaped end of a link 55 or rod which forms a part of the controlled element IS. The link 55 is biased downward by a loading spring 55 which has an upper end bearing against the cover 5| and a lower end bearing against a plate 51 secured to the link. The loading spring forces the bottom plate 53 downward towards a seat, or, from another viewpoint, prevents collapsing of the bellows due to external pressure acting thereon. The upper end of the link 55 projects through an opening 58 in the left-hand portion of the lever 33. The link 55 is connected to the lever 33 by a spring 59 which has an upper turn bearing against the lower side of the lever 33. An intermediate turn of the spring 59 is fastened to a screw-threaded portion 68 of the link 55 by means of a screw clamp 8|. The clamp 5| has a portion fastened to the screw-threaded link portion 88 by means including a screw 82 and an outer portion fastened to an intermediate turn of the spring 59 by a means including a screw 53. By loosening of the screws 52 and 53 the spring clamp may be turned up or down whereby the number of effective turns of the spring 59 between the screw clamp and the lever 33 may be varied. The regulating spring 59 is made comparatively strong in order to insure stability by large instantaneous regulation.

The arrangement includes means for supplying fluid under pressure such as oil to the hydraulic motor 49, the pressure of the fluid being varied by positioning of the variable orifice cup valve 38. Fluid is supplied to the channel 39 from a source of fluid under pressure, not shown, through a pipe screwed into the lower end of the casing 2|. An orifice or restriction 55 is provided near the discharge end of the tube 54. During normal operation, with the mechanism balanced, the cup valve 38 is in a fixed opening position. The fluid passing through the opening formed between the cup valve and its seat is discharged through channels 88 formed in the bottom of the casing and communicating with a discharge conduit 8'! which surrounds the supply conduit 64. The upper end portion of the discharge or drain conduit 81 is screw-threaded into a flanged cup 55, which latter is'fastened to the bottom of the casing by bolts 59.

The arrangement so far described permits ordinary regulation of fluid pressure in the exhaust conduit of the turbine in Fig. l. The various elements described remain in a fixed position as long as the pressure in the turbine exhaust conduit is constant. Now if the pressure in the turbine exhaust conduit increases, due for instance to decrease in demand for exhaust steam, this increase in pressure is transmitted through the pipe H to the pressure responsive device 24 and causes collapsing of the bellows 21. This effects downward movement of the link 3| and counter-clockwise movement of the lever 33 about its fulcrum 34 whereby the link 31 forces the cup valve downward towards closing position. This closing movement reduces the flow of fluid past the cup valve or, from another viewpoint, increases the restriction formed by the cup valve and thereby raises the pressure within the channel 39 and the hydraulic motor 48. Increase in pressure on the bellows 49 of the hydraulic motor efl'ects collapsing of the bellows against the force of the loading spring 58.. This in turn causes upward movement of the link 55 until the increased compression in the spring 59 forces the lever 33 in a clockwise direction sufliciently to open the valve 38 and re-establish the normal balance of the mechanism. The travel of the link 55 simultaneously causes the turbine inlet valve II to move in the closing direction thus bringing the pressure in the turbine exhaust casing back to its proper value.

The regulation of the mechanism so far de scribed which may be termed main governing mechanism" is corrected or compensated by the provision of means including an auxiliary hydraulic motor 19 connected to the right-hand end portion of the governor lever 33. The hydraulic motor 18 is similar to the main hydraulic motor 48 and comprises a bellows disposed within a chamber orcylinder 12, which latter communicates through a channel 13 including a needle valve I4 with the aforementioned channel 41. The upper end of the bellows 1| is rigidly secured to a flanged cylinder I5 provided with a cover 18 and secured to a seat formed by the casing 2|. The bellows contains a loading spring 11 biasing the bellows downward towards a seat 18 formed by the casing and during operation preventing the bellows from collapsing by the pressure of operating fluid contained in the chamber 12. The lower end plate of the bellows contains a conical pivot bearing 19 engaged by the conically shaped end of a rod 88. The upper portion of the rod 38 is screw-threaded and connected by a spring clamp 8| to an intermediate turn of a correcting or compensating spring 82 concentrically surrounding the rod 98 and bearing at its upper end against the lower side of a recessed opening 83 in the right-hand portion of the lever 33. The upper side of the recessed opening 83 in the lever 33 is engaged by the lower end of a loading spring 84. The upper end of the spring 84 bears against a spring plate 85 held on a screw-threaded rod 85 and guided and prevented from rotation by guide posts 91 and 88 secured to the cover 22. The upper end of the rod 95 is provided with a handwheel 89 and held against vertical movement by a flanged support 98 which in turn is secured to the cover 22. Rotation of the handwheel 99 causes vertical movement of the spring plate 95 and thereby changes the compression of the loading spring 84. The characteristic of the correcting or compensating spring 82 may be changed by moving the'spring clamp 9| up or down to strengthen or to weaken the spring 82.

The operation of the mechanism is as follows: With the needle valve 14 in closed position to shut of! communication between the channel 41 and the hydraulic motor chamber 12 the operation is that of an ordinary governing mechanism as described above, that is the pressure in the exhaust casing will slightly increase as the flow decreases. With the needle valve 14 in opening position an increase in exhaust pressure causes downward movement of the left-hand end of the lever 33 which moves the cup valve 38 towards closing position to increase the pressure in the desired value.

ment oi the rod 55, resulting in closing movement of the" turbine inlet valve. The pressure in the I exhaust casing then will be above its normal value by the amount of regulation of the governor. Now with the needle valve 14 slightly open, the increase in pressure in the channel 41 also causes a gradual increase in pressure in the chamber 12. forcing the bellows H upward against the biasing force of the loading spring 1.1 thus increasing the force which spring 82 exerts on the lever 33. This increase in force tends to compensate for the normal regulation of the governor. The number of effective turns in the spring 82 determines the amount of compensation that is accomplished. The needle valve I4 limits the rate at which this compensation takes place, thus insuring stable operation. The closing movement of the turbine inlet valve causes a drop in exhaust pressure and consequently a decreasing force onto the lever -33 by the rod 3| oi. the pressure responsive device until the decreasing force balances the force exerted onto the ends of the lever 83 by the hydraulic motors. As such balance is attained, the mechanism is in equilibrium and no further movement will take place until the exhaust pressure changes again. Thus, briefly, it the exhaust pressure increases, the main governing mechanism causes closing movement of the cup valve 38, resulting in closing movementof the turbine inlet valve and the correcting or compensating or auxiliary mechanism causes an additional closing of the cup valve 38, resulting in an additional closing movement of the turbine inlet ,valve to bring the pressure in the exhaust casing back to the The two movements naturally take place simultaneously, the main mechanism including the hydraulic motor 48 acting quickly, while the auxiliary or correcting mechanism acts slowly, the slow action or time delay of the latter depending upon the position of the needle valve 14, which latter determines the rate of increase in I regulation.

such mechanisms may be readily varied. The particular mechanism described above is free from any pin connections. Instead, the various elements are connected by links with conical pivots engaging corresponding bearings. This reduces considerably the friction of the apparatus and increases accordingly its accuracy and sensitivity. The entire mechanism includes only a single lever Bland is-free i rom movable or ad- I justable fulcrums heretofore providd in mechanisms of this kind. Changes in either instantaneous or final regulationof the mechanism are made by changing the number of turns in the regulating spring 59 and the correcting spring 82. By turning the spring clamps 83 and 8|, the regulation may be changed by infinitely small steps. In other words, the apparatus permits a gradual change of the regulation as distinguished Only extremely small from a stepped change. travel of the pressure responsive element 24 is needed for accurate control of the turbine inlet valve. The entire movement of the pressure responsive device 24 may be 10 mils and less. The extremely small travel prolongs the life of the pressure responsive element.

The regulation is changed by changing the characteristic in the system rather than changing the effective stroke of the operating element whereby substantially the same degree of accuracy is maintained for any degree 01' regulation. The correcting mechanism may be adjusted to undercorrect or overcorrect that isto under compensate or overcompensate respectively the instantaneous Having described the method of operation of my invention, together with the apparatus which I now consider to represent the best embodiment thereof. I desire to have it understood that the pressure in the chamber 12 of the auxiliary hY- draulic motor in response to pressure increase pressure changes in a predetermined manner inv response to load changes on the turbine between no load and full load. Thus, for example, it the regulation of the main governing mechanism including the motor 49, 55, the device 24, 80 and the control valve 38, 28 is 4%, meaning that during change of load from no load to full load the pressure in the exhaust will decrease by 4% with the auxiliary or correcting mechanism out of operation, that is, with the needle valve 14 in closed position, this regulation cl. 4% may be varied or corrected by opening the needle valve 14 so that the pressure variation between no load and full load will decrease to any desired value or become zero. The pressure which the pressure governor holds at the exhaust casing of the turbine is adjusted by changing the compression of the'spring 84.

With my invention I have accomplished an apparatus shown is only illustrative and that the invention may be carried out by other means.

What I claim asnew and desire to secure by Letters Patent of the United States is:

1. Governing mechanism comprising a controlling element, a controlled element, regulating means including a hydraulic motor formoving the controlled'element in response to movement of the controlling element, and adjustable means directly responsive to the controlling element for compensatingthe regulation or the regulating means and including another hydraulic motor ment of the motor in response to changes of a to movement of the lever, an adjustable spring connecting the stem to the lever, and auxiliary.

- means responsive to the change in fluid pressure for effecting additional movement of the motor.

4. Governing mechanism comprising a i'ulcrumed lever, a device responsive to a condition to be controlled and connected to the lever, a hydraulic motor having a stem connected to the lever, means including a cup valve connected to the lever for controlling movement of the motor in response to movement of the device, and auxiliary means including a second motor hydraulically connected to the flrst motor and to the lever and responsive to the change in fluid pressure in the flrst motor for efiectlng additional movement of the first motor;

5. Governing mechanism comprising a 111- crumed lever, a pressure responsive device connected to the lever, a hydraulic motor with a stem, means including a spring adjustably connecting the stem to the lever,'a source of fluid under pressure connected to the motor, means including a variable orifice connected to the lever to effect movement of the motor in response to movement of the pressure responsive device, and auxiliary means responsive to the change in fluid pressure for effecting additional movement 01' the motor.

6. Governing mechanism comprising a fulcrumed lever, a pressure responsive device connected to the lever, a hydraulic motor with a stern, means including a spring adjustably connecting the stem to the lever, a source of fluid under pressure connected to the motor, means including a variable orifice connected to the lever to effect movement of the motor in response to movement of the pressure responsive device, and auxiliary means responsive to the change in fluid pressure for effecting additional movement of the motor, said auxiliary means comprising another motor hydraulically connected to the first motor and adjustable spring means connecting the other motor to the lever.

7. Governing mechanism with adjustable regulation' including the combination of a controlled element, a controlling element, and means for moving the controlled element in response to movement of the controlling element, said means comprising a tulcrumedlever pivotally connected to the controlling element, a first and a second hydraulic motor, a source of fluid under pressure connected to the first motor, means including a control valve connected to the lever for controlling the fluid pressure in the first motor, a conduit with a valve directly connecting the second motor to the first motor whereby the fluid pressure in the second motor varies in response to movement of the control valve, and. adjustable spring means connecting the motors to'the lever.

8. Governing mechanism comprising the combination of a lever, a device connected to the lever and responsive to changes of a condition to be controlled, two hydraulic motors connected to the lever, a source or fluid under pressure. a control element connected to the lever and controlling the flow of fluid from the source to both motors, and means for controlling the rate of flow of fluid under pressure to one of the motors with relation to the rate of flow to the other motor.

9. Governing mechanism comprising a fulcrumed lever, a device connected'to the lever and responsive to changes of a condition to be controlled, a flrst hydraulic motor having a piston with a stem for connection to an element to be controlled and 'yieldable means for connecting the stem to the lever, a second hydraulic motor having a piston with a stem and a means yieldably connecting the stem to the lever, means including a; channel connected to both motors for conducting operating fluid thereto, and a control member connected to the lever for controlling the fluid pressure in the channel.

FRANCIS H. VAN NEST. 

